EP1048374B1 - Dispositif d'enroulement de ressorts, en particulier pour machines d'enroulement de ressorts - Google Patents

Dispositif d'enroulement de ressorts, en particulier pour machines d'enroulement de ressorts Download PDF

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Publication number
EP1048374B1
EP1048374B1 EP00104664A EP00104664A EP1048374B1 EP 1048374 B1 EP1048374 B1 EP 1048374B1 EP 00104664 A EP00104664 A EP 00104664A EP 00104664 A EP00104664 A EP 00104664A EP 1048374 B1 EP1048374 B1 EP 1048374B1
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EP
European Patent Office
Prior art keywords
winding
cam
winch
slide
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00104664A
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German (de)
English (en)
Other versions
EP1048374A3 (fr
EP1048374A2 (fr
Inventor
Dietmar Sautter
Karl-Heinz Fritz
Joachim Baermann
Franz Decker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wafios AG
Original Assignee
Wafios AG
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Filing date
Publication date
Application filed by Wafios AG filed Critical Wafios AG
Publication of EP1048374A2 publication Critical patent/EP1048374A2/fr
Publication of EP1048374A3 publication Critical patent/EP1048374A3/fr
Application granted granted Critical
Publication of EP1048374B1 publication Critical patent/EP1048374B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F3/00—Coiling wire into particular forms
    • B21F3/02—Coiling wire into particular forms helically

Definitions

  • the invention relates to a spring winch device, in particular for spring winch machines, for the production of either right-hand or left-hand coil springs made of wire.
  • each of the two winches is pivotally mounted about a bearing axis which runs transversely to the axis of the wire guide and is located on the end section of the slide guide body facing away from the wire guide.
  • This known spring winch device makes it possible that each tool moves linearly and at the same time swivels and can thus be used both as an internal and as an external winding tool. It is possible to change the wind direction without having to replace the entire winch.
  • no control means are provided to the two To be able to move wind tools against each other during the manufacture of springs, it is not possible to produce shaped springs with this known device.
  • a winch device which can not only be used for the production of either right-hand or left-hand helical coil springs, but is also suitable for producing acylindrical helical springs, is described in DE-GM 92 13 164.
  • Two winch devices are also used, each of which has a carriage guide body, in which a carriage is displaceably arranged so that a winch tool connected to the carriage is guided in a linearly movable manner relative to the wire exit point of the wire from the wire guide.
  • Each carriage guide body can be pivoted at its end region facing away from the wire guide about a pivot axis directed perpendicular to the wire guide axis and parallel to a central plane running through the wire guide axis, both winch apparatuses being arranged on different sides of this central plane.
  • Each of the two winch devices is assigned its own cam mechanism, which in one winch device pushes the carriage back and forth in its guide, while in the other winch device it swings the carriage guide body back and forth and both movements are program-controlled with respect to one another.
  • the invention has for its object to provide a spring winch device of the type mentioned, in which the change of the wind direction of the springs produced is possible while largely avoiding mechanical changeover work, and which nevertheless has a relatively simple structure.
  • a spring winch device in particular for spring winch machines, for the production of either right-hand or left-hand helical coil springs made of wire, with feed rollers for conveying the wire along a wire guide axis through a wire guide, with two winch apparatuses, each of which has a slide guide body in which one Carriage is slidably arranged so that a winch tool connected to the carriage is linearly movable relative to the wire exit point of the wire from the wire guide, with each carriage guide body at its end region facing away from the wire guide about a perpendicular to the wire guide axis and parallel to a central plane running through the wire guide axis
  • Directional pivot axis is pivotable, both winches are arranged on different sides of this central plane, each winch is a drive for moving the carriage and one of one Cam-controlled cam mechanism is assigned for pivoting the carriage guide body about the pivot axis, the cam mechanisms of both winches being assigned a common cam disc that can be pivoted by
  • the manufacture of non-circular springs is possible, a reduced adjustment effort and the repeatability of settings are ensured, and the spring can be automatically wound without manual intervention for the first winding.
  • a common cam plate assigned to the two cam mechanisms which only has to be rotated by a certain angle to switch on one or the other cam mechanism, this is Conversion effort to change from right-hand to left-hand winches minimized, since only the individual tool settings have to be made on the tool holder.
  • the spring winch device according to the invention there is also an increased rigidity of the overall arrangement due to a more favorable flow of force and the increased assembly and maintenance expenditure for the belt drive, as is required in the arrangement from DE-GM 92 13 164. It is also possible with the spring coiling machine according to the invention to achieve a constant load torque over the entire spring diameter range (with the same wire diameter and based on the forming forces) by using a specially calculated curve law.
  • cam disk used in the invention which is common to both cam drives, leads to the fact that only three servomotors have to be provided in total, and the entire basic principle of the spring winch is thereby covered with three axes. All advantages can only be achieved by using a third motor, without the need to use a further motor, as is used in the known spring winch device according to DE-OS 198 25 970.
  • the complicated arrangement of stacked tables which are also used in this prior art and can be moved relative to one another in different directions, for the tool carrying devices and the, likewise quite complicated connection mechanism on the one table, which, when a second table moves, moves two further tables is required to be completely dispensed with.
  • the individual motors for driving the common cam as well as for the two drives for moving the slides are coupled to one another via an electronic program control, which ensures that the motors used for the winding of Fedem in one direction of wind each carry out the movements that are program-controlled precisely are required for the production of the desired spring shape.
  • the cam mechanism of one winch apparatus works with the drive for the movement of the carriage of the other winch apparatus in a program-controlled manner, as a result of which coil springs of a wind direction can be produced in the two-finger system. If springs of the other wind direction are to be generated, the cam mechanism of the other winch device is interconnected with the other drive for the linear movement of the slide.
  • the cam mechanism of a winch device is preferably program-controlled coupled to the drive for the movement of the carriage of the same winch device, i.e. one winch is in use while the other winch is inactive.
  • the cam mechanism of the other winch device is preferably program-controlled coupled to the drive for the movement of the carriage in this winch device.
  • any suitable type of drive can in principle be used as the drive for the movement of the carriage in any winch apparatus. It is very particularly preferred, however, if a cam which can be rotated by a program-controlled motor is provided as the drive for the movement of the carriage in each winch apparatus, the cam movement of which is transmitted to the carriage in a force-controlled manner. This has the great advantage that, due to the positive guidance, the weight and acceleration forces that occur do not impair the accuracy of the movement of the slide or tool holder.
  • the axis of rotation of the cam disk common to the two cam drives is particularly preferably arranged in such a way that it intersects the extension of the wire guide axis perpendicularly and lies in the central plane.
  • the winch apparatuses are also arranged mirror-symmetrically to the wire guide axis, whereby - again preferred - they are designed mirror-like to one another.
  • a guide plate is attached between the winch apparatus and symmetrically to the wire guide axis in its extension and at a distance from the wire exit point, which has a guide track on both of its sides facing the winch apparatus, on which the facing end of the slide guide body of the concerned winch slides.
  • the spring winch device 10 shown by way of example in its structural details is part of a spring winch machine (not shown) with feed rollers 12 driven by a CNC-controllable servo motor (not shown), which feed a wire 14 straight and horizontally through a wire guide 16 into a wind station 18, in which the wire 14 through two winch tools 20 and 22, which are designed in the form of winch fingers, from two winch attachments 30 and 32 fastened to one another on a winch plate 26 of the spring winch machine, depending on the position of the two winch tools 20 and 22, to right-hand or left-hand winders Coil springs is molded, ie Depending on whether a right-hand or a left-hand coil spring is to be produced, the wire 14 is deflected upward or downward with respect to the wire guide axis 34.
  • Each of the two above and below the wire guide axis 34 and a winch apparatus 30 and 32 arranged through this center plane MM consists of a slide guide body 36 and 38, on which a slide 40 and 42 by means of a commercially available linear guide unit 43, the guide rail of which is attached to the slide guide bodies 36 and 38 and the guide carriage of which are attached to the slide 40 and 42, is longitudinally displaceable.
  • Each of the slides 40, 42 carries, at its end facing the wire guide 16, a pivotally mounted holder 44 or 46 in which the upper winch tool 22 or the lower winch tool 24 is fastened
  • Each of the two slide guide bodies 36 and 38 is pivotally mounted on its end region facing away from the winch tool 22 or 24 on an axis designed as a frame-fixed bolt 48 or 50 on the winch plate 26.
  • the tool-near end of each slide guide body 36 or 38 is rounded with a radius around the axis of the bolt 48 or 50. With these ends, both slide guide bodies 36 and 38 lie on a coplanar guide plate 52 with lateral tracks 54 facing the slide guide bodies 36 and 38 accordingly designed, concave contour on both sides.
  • a gear 60 and 62 is centered in a receiving bore, to each of which a program-controlled, intermittently back and forth rotating servo motor 64 or 66 is flanged on the input side.
  • a control cam 68 and 70 is rotatably connected to the drive shafts of the two gears 60 and 62.
  • two rollers 72 and 74 each run, which are each rotatably arranged on a bolt 76 and 78 fastened to the upper slide 40 and lower slide 42 (FIG. 2), as a result of which the movement of the Carriage 40 and 42 is forcibly guided by the rotary movement of the control cams 68 and 70.
  • a further gearbox 84 is flanged in the winch plate 26 of the spring coiling machine in a remote receiving hole perpendicular to the wire guide axis 34, with its central axis passing through this and lying in the central plane MM, at the input of which another CNC-controllable, intermittent forward and backward rotating servo motor 86 is attached.
  • a disk-shaped control cam 88 which is designed as a bead curve and on which two rollers 90 and 92 each run in a positively guided manner, is seated on the gearbox 84 in a rotationally fixed manner, each of which has an angular, one-armed lever 98 and 100 are rotatably arranged.
  • the two bolts 94 and 96 are arranged on different sides of the drive shaft of the gear 84 and at the same distance from it, perpendicular to the wire guide axis 34, one above the other (FIG. 3).
  • one coupling articulated rod 106 and 108 is articulated by means of bolts 110 and 112 on the one hand approximately centrally on the lever 98 and 100 on the other hand and on the other hand by means of bolts 114 and 116 on the slide guide body 36 of the upper winch apparatus 30 and on the slide guide body 38 of the lower winch apparatus 32.
  • the servomotor 64 is activated, which drives the control cam 68 program-controlled, intermittently rotating forward and backward.
  • the radial movement of the control cam 68 becomes above the rollers 72 transferred to the carriage 40 of the upper winch apparatus 30 and the upper winch tool 20 is moved linearly back and forth in a closer / front or further / rear oblique position relative to the wire exit point of the wire 14 on the wire guide 16
  • the movement of the wind tool 22 of the lower winch apparatus 32 is predetermined by the control cam 88, which is correspondingly driven by the servo motor 86 via the gear 84.
  • the movement of the control cam 88 is transmitted via the rollers 92 to the pivotable lever 100 and further via the coupling articulated rod 108 to the lower slide guide body 38.
  • the slide guide body 38 guides a positively controlled to and fro with the winch tool 22 of the lower winch apparatus 32 pivotal movement about the axis of the bolt 50 as a pivot center.
  • the lower winch tool 22 is thus also moved to a front and rear position with respect to the wire exit point on the wire guide 16 by means of the cam mechanism 88, 92 and 100.
  • the winch tools 20 and 22 of the upper and lower winch apparatus 30 and 32 are shifted (at least predominantly) at the same time according to a structurally determined law.
  • the specially calculated curve laws of the two control cams 68 and 88 in conjunction with the two program-controlled, intermittently forward and reverse rotating servomotors 64 and 86 are used for this purpose.
  • control curve 88 in addition to two control sections, which are used to initiate control movements in one or the other of the two Cam gear are designed, provided over certain areas of their circumference with two locking sections, ie above this rotation range of the curve of the control cam 88 there is no control movement on the transmission members.
  • the latching section of the control cam 88 is responsible or effective for the upper winch apparatus 30, which therefore does not perform a pivoting movement about the bolt 48 here.
  • the upper winding apparatus 30 is also rigidly fixed via the cam roller 90, the lever 98 and the coupling joint rod 106 and their connecting bolts 110 and 114.
  • the CNC-controllable servo motor 66 of the lower winch apparatus 32 is switched off in a program-controlled manner when winds to the right. However, it can be used to automatically bend the first wire winding through the lower winding tool 22.
  • the servomotors 64 and 66 move after inputting "left-hand winds" the upper and lower winch tools 20 and 22 in their rearmost position, which is most retracted from the wire guide 16, while the servo motor 86 then continues to turn the control cam 88 until the Locking section of the control cam 88 is now effective for the lower winch 32.
  • the subsequent setting of the initial diameter of a form spring or the outside diameter of a cylindrical helical spring is then carried out by switching on both servomotors 64 and 66, which legally shift the winding tools 22 and 24 to one another to the required extent.
  • the drive motor 64 of the upper winch apparatus 30 is switched off or used for the automatic bending of the wire of the first spring turn by the upper winch tool 20.
  • the coordinated movement of the winch tool 20 of the upper winch apparatus 30 required for producing a left-hand shaped spring is carried out via the control cam 88 driven by the servo motor 86.
  • the transmission of the control cam 88 is now carried out via the two rollers 90 to the pivotable lever 98 and further above the coupling joint rod 106 and the bolts 110 and 114 on the upper slide guide body 36, which thereby swings back and forth about the axis of the bolt 48 as the pivot center and thus moves the winch tool 20.
  • the linear movement of the lower winch tool 22 takes place through the control cam 70 driven by the servo motor 66 via the rollers 74 and the slide 42.
  • the winch tool 20 of the upper winch device 30 now serves as an inner tool in the manufacture of left-hand wound spring bodies and the winch tool 22 of the lower winch device 32 as an outer winch tool; while for right-hand coil springs, the upper tool 20 serves as an external winding tool and the lower tool 22 serves as an internal winding tool ("inside” and "outside” being used in accordance with the terminology given in DE-OS 2 310 174).
  • FIGS. 6 and 7 show the spring winch device set up for producing right-handed coil springs in the single-finger winch system.
  • the motorized movement of the only winch tool 120 here takes place in two directions of movement, as is described in more detail below with reference to FIGS. 1 to 7.
  • the only winch tool 120 is fastened to a holder 122 on the slide 40 of the upper winch apparatus 30, the slide 40 being forcibly guided back and forth via a cam disk 68 and rollers 72 seated on bolts 76.
  • the cam disk 68 itself is driven intermittently back and forth by the program-controlled servo motor 64 (FIG. 7) via the gear 60.
  • a program-controlled swiveling movement of the upper slide guide body 36 about the axis of the bolt 48 as a swiveling center takes place (or can take place).
  • This pivoting movement is transmitted by a CNC-controllable servo motor 86 via a gear 84 to a control cam 88 (as shown in FIG. 3) and from there via two rollers 90 to the lever 98 pivotable on pin 94 and further via a coupling articulated rod 106 via bolts 110 and 114 to a slide guide body 36 of the upper winch apparatus 30.
  • the carriage 42 of the lower winch apparatus 32 which is inactive for production here and whose winch tool holder is removed, was moved into its retracted rear position by the servo motor 66 (as in FIG. 2) and the control cam 70.
  • the lower winch 32 is in use to produce left-hand coil springs in the single-finger winch system, while the upper winch 30 is now inactive.
  • the straight line movement of the winch tool, not shown, now takes place from the servo motor 66 from above the cam plate 70, and the pivoting movement of the lower slide guide body 38 about the bolts 50 from the servo motor 86, which previously rotated the control cam 88 so far that its locking area is now for the upper inactive winch apparatus 30 is responsible, above this control curve 88 on the lever 100 and from here above the coupling articulated rod 108 on the slide guide body 38.
  • left-hand coil springs can also be produced with the winch tool 120 of the upper winch device 30. All that is required is that the winding apparatus 30 has been moved upwards by the servo motor 64 so that the winding tool 120 now engages the wire 14 on the other side, that is to say above the wire guide axis 34, and acts downward, while for the previously coiled coil springs, this Winding tool 120 attacked wire 14 below wire guide axis 34 and moved upward.
  • the two winch apparatuses 30 and 32 are arranged mirror-symmetrically to the wire guide axis 34 on the winch plate 26 and are designed to be mirror-like to one another.
  • non-circular helical springs can also be produced by the separate control of the winch tools, or it is possible to wind spring forms which have different wind radii within one spring turn.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Wire Processing (AREA)
  • Gears, Cams (AREA)
  • Springs (AREA)

Claims (9)

  1. Dispositif d'enroulement de ressorts, en particulier pour machines d'enroulement de ressorts, pour la fabrication de ressorts hélicoïdaux en fil métallique, enroulés au choix à droite ou à gauche, comportant des cylindres d'introduction (12) pour le transport du fil (14) le long d'un axe de guidage de fil (4) par un guide-fil (16), comportant deux appareils d'enroulement (30 ; 32) dont chacun comporte un corps de guidage à chariot (36 ; 38) dans lequel un chariot (40 ; 42) est disposé coulissant de manière qu'un outil d'enroulement (20 ; 22) relié au chariot (40 ; 42), est guidé déplaçable linéairement par rapport au point de sortie du fil (14) du guide-fil (16), chaque corps de guidage à chariot (36 ; 38) pouvant pivoter, dans sa zone d'extrémité tournée à l'opposé du guide-fil (16), autour d'un axe de pivotement (48 ; 50) perpendiculaire à l'axe de guidage du fil (34) et parallèle au plan médian (M-M) passant par l'axe de guidage du fil (34), les deux appareils d'enroulement (30 ; 32) étant disposés sur différents côtés de ce plan médian (M-M), un dispositif d'entraînement (64, 68 ; 66, 70) pour le déplacement du chariot (40, 42) et un mécanisme à cames (90, 98, 106 ; 92, 100, 108), commandé par un disque à cames (88), pour le pivotement du corps de guidage à chariot (36 ; 38) autour de l'axe de pivotement (48 ; 50) étant associés à chaque appareil d'enroulement (30; 32), un disque à cames (88) commun, étant associé aux mécanismes à cames (90, 98, 106; 92, 100, 108) des deux appareils d'enroulement (30; 32) pouvant pivoter au moyen d'un moteur (86) programmé, avec deux tronçons de commande et au moins un tronçon d'accrochage, chaque tronçon de commande étant conçu pour introduire des mouvements de commande dans l'un des deux mécanismes à cames (90, 98, 106 ; 92, 100, 108), et chaque tronçon d'accrochage pour ne pas introduire de mouvements de commande dans les mécanismes à cames (90, 98, 106 ; 92, 100, 108), et par rotation du disque à cames (88), l'un des tronçons de commande pouvant être appliqué contre le mécanisme à cames (90, 98, 106 ; 92, 100, 108) associé pour sa commande, en vue de la réalisation de ressorts hélicoïdaux dans un sens d'enroulement, tandis que l'autre mécanisme à cames (92, 100, 108 ; 90, 98, 106) s'applique contre le ou un tronçon d'accrochage, et le mécanisme à cames commandé (90, 98, 106 ; 92, 100, 108) coopérant de manière commandée par programme avec le dispositif d'entraînement (64, 68 ; 66, 70) pour le mouvement de l'un des chariots, tandis que le dispositif d'entraînement (66, 70 ; 64, 68) de l'autre chariot (42 ; 40) est à l'arrêt.
  2. Dispositif d'enroulement de ressorts selon la revendication 1, dans lequel le mécanisme à cames (90, 98, 106 ; 92, 100, 108) de chaque appareil d'enroulement (30 ; 32) coopère, de manière commandée par programme, avec le dispositif d'entraînement (64, 68 ; 66, 70) pour le déplacement du chariot (40 ; 42) de l'autre appareil d'enroulement (32 ; 30).
  3. Dispositif d'enroulement de ressorts selon la revendication 1 ou 2, dans lequel il est prévu comme dispositif d'entraînement pour le déplacement du chariot (40 ; 42) de chaque appareil d'enroulement (30 ; 32), un disque à cames (68, 70) qui peut tourner au moyen d'un moteur (64 ; 66) commandé par programme.
  4. Dispositif d'enroulement de ressorts selon la revendication 3, dans lequel le chariot (40 ; 42) de chaque appareil d'enroulement (30 ; 32) est guidé forcé sur le disque à cames (60 ; 70) tournant.
  5. Dispositif d'enroulement de ressorts selon l'une des revendications 1 à 4, dans lequel l'axe de rotation du disque à cames (88), commun aux deux mécanismes à cames (90, 98, 106 ; 92, 100, 108), se situe dans le prolongement de l'axe de guidage du fil.
  6. Dispositif d'enroulement de ressorts selon l'une des revendications 1 ou 3 à 5, dans lequel le mécanisme à cames (90, 98, 106 ; 92, 100, 108) d'un appareil d'enroulement (30 ; 32) coopère, de manière commandée par programme, avec le dispositif d'entraînement (64 ; 66) pour le déplacement du chariot (40 ; 42) de ce même appareil d'enroulement (30 ; 32).
  7. Dispositif d'enroulement de ressorts selon l'une des revendications 1 à 6, dans lequel est placée, entre les appareils d'enroulement (40 ; 42) et symétriquement à l'axe de guidage du fil (34), dans le prolongement de ce dernier ainsi qu'à distance du point de sortie du fil, une plaque de guidage (52) qui comporte, sur chacun de ses deux côtés tournés vers les appareils d'enroulement (30, 32), une voie de guidage (54) sur laquelle glisse l'extrémité, tournée vers celle-ci du corps de guidage à chariot (36 ; 38) de l'appareil d'enroulement (30 ; 32) concerné.
  8. Dispositif d'enroulement de ressorts selon l'une des revendications 1 à 7, dans lequel les appareils d'enroulement (30, 32) sont disposés dans une symétrie en miroir par rapport au plan médian (M-M).
  9. Dispositif d'enroulement de ressorts selon l'une des revendications 1 à 8, dans lequel les appareils d'enroulement (30, 32) sont réalisés symétriques l'un à l'autre.
EP00104664A 1999-04-30 2000-03-03 Dispositif d'enroulement de ressorts, en particulier pour machines d'enroulement de ressorts Expired - Lifetime EP1048374B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19919956A DE19919956C1 (de) 1999-04-30 1999-04-30 Federwindeeinrichtung, insbesondere für Federwindemaschinen
DE19919956 1999-04-30

Publications (3)

Publication Number Publication Date
EP1048374A2 EP1048374A2 (fr) 2000-11-02
EP1048374A3 EP1048374A3 (fr) 2002-02-06
EP1048374B1 true EP1048374B1 (fr) 2004-04-28

Family

ID=7906579

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00104664A Expired - Lifetime EP1048374B1 (fr) 1999-04-30 2000-03-03 Dispositif d'enroulement de ressorts, en particulier pour machines d'enroulement de ressorts

Country Status (4)

Country Link
US (1) US6393888B1 (fr)
EP (1) EP1048374B1 (fr)
JP (1) JP3486598B2 (fr)
DE (2) DE19919956C1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4403109B2 (ja) 2005-06-21 2010-01-20 新興機械工業株式会社 ばね製造機
CN100418663C (zh) * 2005-11-01 2008-09-17 自如行自动化有限公司 弹簧成型机结构改良的抵推装置
DE102010014353B3 (de) * 2010-04-09 2011-06-16 Wafios Ag Vorrichtung zur Herstellung einer Öse an einem Ende einer Schraubenfeder
CN102825180B (zh) * 2012-09-13 2014-10-29 东莞市开创精密机械有限公司 一种刀架一体化的卷簧机
KR102344335B1 (ko) * 2021-07-12 2021-12-27 조현종 코일 스프링 성형 방법

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE896186C (de) * 1938-07-20 1953-11-09 Wafios Wagner Maschf Verstellvorrichtung fuer Windewerkzeuge an Federwindemaschinen
DE2310174A1 (de) * 1973-03-01 1974-09-05 Hack Karl Maschf Federwindemaschine
US3934445A (en) * 1974-06-24 1976-01-27 Torin Corporation Dual purpose spring coiling machine
US4872854A (en) * 1988-03-23 1989-10-10 Hyman Products, Inc. Simulated ball used in sports incorporating an electronic component
DE4138896A1 (de) * 1990-12-19 1992-07-02 Wafios Maschinen Wagner Universal-federwindemaschine mit schneideinrichtung
DE9213164U1 (de) * 1992-09-30 1993-01-14 WAFIOS Maschinenfabrik GmbH & Co KG, 7410 Reutlingen Windeeinrichtung für Drahtform-Vorrichtungen, insbesondere Federwindemaschinen
DE19611661C2 (de) * 1996-03-25 1998-09-10 Wafios Maschinen Wagner Vorrichtung zum Formen von Draht, insbesondere Universal-Federwindemaschine
US6000265A (en) * 1997-06-10 1999-12-14 Kabushiki Kaisha Itaya Seisaku Sho Spring manufacturing apparatus

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Publication number Publication date
JP2000317563A (ja) 2000-11-21
DE50006211D1 (de) 2004-06-03
EP1048374A3 (fr) 2002-02-06
DE19919956C1 (de) 2000-07-06
EP1048374A2 (fr) 2000-11-02
JP3486598B2 (ja) 2004-01-13
US6393888B1 (en) 2002-05-28

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